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The Ford Flathead Engine
How Too Size A Turbo-Charger
For Our Application...
Project:
Flathead is going to be Turbo-Charged, so we need to know how to choose the correct Turbo
for the engine we have. Were starting out with a Ford Flat-Head Engine, it has 235 ci, 8-Cylinders and is a 4-Stroke.
Configuration = V-8 Cubic Displacement = 235 ci Bore = 3.1875" Stroke
= 3.750" Ambient Temperature = 70°f
Barometer = 29.0 in Hg Maximum RPM (a) = 5,000 rpm
(b) = 6,000 rpm Maximum Boost Pressure
(a) = 7psi (b) = 14.2 psi I will be tracking the conditions of two separate scenario's, I think this will add
Balance and allow some interesting comparisons. Let's start by Converting the Displacement of our Engine from cubic inches to cubic feet
Converting the Displacement
235ci
= 0.1359 cu ft
1728 cu in/cu ft Airflow Rate - Airflow
rate through an engine is referred to as cubic feet per minute (CFM) at a standard atmospheric pressure. Next we will Calculate the
Ideal Volume Flow through our Engine Ideal Volume Flow Engine
(a) 0.1359 cu ft x
5000 rpm = 339.75 cfm
Revolutions
2 Engine (b)
0.1359 cu ft x 6000 rpm
= 407 cfm Revolutions 2
These figures
above are at 100% Efficiency, because of Residual Gases, Intake and Cylinder Head restrictions most Engines don't operate
at 100% Efficiency, a more realistic figure for our Engine would be 80% Efficiency. Converting to 80% Efficiency Engine (a) 339.75 x .80 = 271.8 cfm Engine (b) 407
x .80 = 325.6 cfm Another way to determine the Air Flow rate is by the following: Airflow rate = CID x rpm x 0.5 x Ev (80%)
1728 Engine (a) Air Flow
Rate = 235cid x 5000rpm x 0.5 x 0.80
1728 Air Flow Rate = 470000
= 271.99 cfm
1728
Engine (b)
Air Flow Rate = 235cid x 6000rpm
x 0.5 x 0.80
1728 Air Flow Rate = 564000
= 326.38 cfm
1728 With this method, the flow rate is in cfm and the displacement
is in cubic inches. We use .5 because the 4-stroke engine only fills the cylinders once every two revolution,
and the 1728 converts the cubic inches to cubic feet. Both methods will work and both give the Air Flow Rates of Normal,
Turbo-Charged or Super-Charged engines, based on how much air an engine will flow at 80% efficiency. All compressors are rated at Inlet Flow, and air entering
the intake will not be at standard conditions (29.92 in Hg & 60°f) Because of this, it is necessary to compute
the actual density to determine the air flow through the turbochargers compressor. For our application, we will consider
compressor Efficiency to be 65%. First we need to find our Pressure Ratio. Pressure Ratio Pressure Ratio = Manifold Pressure Absolute Inlet
Pressure Absolute (To convert from psi to in Hg you need
to multiply by 2.03) Engine (a) PR
= (7psi x 2.03) + 29.0 = 1.49
29.0 Engine (b) PR = (14.2psi x 2.03) + 29.0 = 1.994
29.0 We got our (Y) figures from the Ideal Temperature
Rise Chart Engine (a)
Y = 0.121 Engine (b)
Y = 0.217 It is also necessary
to add 460f to the temperatures because the calculations need to be in Absolute Temperature (degrees Rankine)
Tideal = Y x T1
Engine (a) Tideal = 0.121 x (70 + 460) =
64.13f Engine (b) Tideal
= 0.217 x (70 + 460) = 115.01f
Actual Temperature Rise Tactual = Tideal
/ Compressor Efficiency (65%) Engine (a) = 64.13f / .65
=98.66f Engine (b)
= 115.01f / .65 =176.93f Intake Manifold Temperature IMT
= Compressor Inlet Temperature + Tactual Engine (a) = 70°f +
98.66°f = 168.66°f Engine (b) = 70°f + 176.93°f = 246.93°f Notice
the huge difference in Temperature between the two (2) engines? Remember, the engines are identical, except for the
higher boost and RPM levels. Engine (b) would absolutely benefit from some sort of Inter-Cooler.
These Intake Air Temperatures may or may not actually get this hot.
There is some cooling effect from the Inter-Cooler tubing, and because fuel itself has an cooling effect on the intake air.
Project:Flat-Head will include the use of Twin-Inter-Coolers,
which will substantially lower this intake Air Temperature. But we have to figure the Theoretical Intake Air Temperature
to get the Density Ratio. Density
Ratio Turbo-Chargers
produce there power by packing more air molecules into the combustion chamber. How tight these molecules are packed
into each cubic inch of volume, is refereed to as the Density of the Air Charge. The Density Ratio is nothing more then comparing the Inlet Temperature to the Outlet temperature,
and the Inlet Pressure to the Outlet Pressure. Density
Ratio = Inlet
Temperature x Outlet Pressure Outlet Temperature Inlet Pressure Engine (a) Density Ratio = 70 + 460 x
14.21+ 29.0
168.66 + 460 29.0
Density
Ratio = 530 x 43.21
628.66 29.0 Density Ratio =
0.84306 x 1.49 Density Ratio = 1.256 Engine
(b) Density
Ratio = 70 + 460 x 28.826 + 29.0
246.93 + 460 29.0 Density Ratio =
530 x 57.826 706.93
29.0 Density
Ratio = 0.7497 x 1.994 Density Ratio
= 1.494 Compressor Inlet Flow Now with this piece of the puzzle solved we can calculate the Actual Compressor Inlet Flow,
under these conditions. Compressor Inlet Flow = Compressor Outlet Flow x Density Ratio
Engine (a)
Compressor Inlet Flow
= 271.8 cfm x 1.256
= 341.38cfm
Engine (b)
Compressor
Inlet Flow = 326 cfm x 1.494
= 487.04cfm
We now have everything we need to find the Turbo-Charger that is right for our engine. Most legitimate Turbo-Charger
retailers will display the Compressor Map for each Turbo-Charger they sell, same goes for the manufacturer, they should make
available each Compressor Map for the various Turbo-Chargers they sell. With the data now "in hand", you can
compare the many different Turbo-Chargers so you find one that works best for your situation. Also, when doing calculations
like these that take into account the Ideal Temperature Rise, where you need the "Y" Data from a table, many
times this table and it's data will be located on the manufacturers or retailers site. If not, call them and they
can provide it for you. Most Compressor Maps are
in cfm, some are in lb/min. Too convert cfm to lb/min simply multiply the cfm figure by 0.069. Also
note that most Compressor Map created for lb/min, are also calculated with the Turbo-Charger at 85°f and a barometer of
28.4 in-Hg. Lets look back
and see what we have found through all these calculations.
On our Project Engine (a)
Approximately 49% more air will be going through the engine
then the engine could have consumed by itself. Engine (b)
will have approximately 99% more air. We find this out
my looking at the Pressure Ratio. Pressure is also measured in bar, and Atmospheres (ATM) ,1 ATM = 1 bar = 14.7psi.
In engine (b) the the PR or Pressure Ratio, of 1.99 is equal
to 1.99 bar. In theory, engine (b) would have an equal
power output of an engine twice the displacement !! that means our little 235 under 14.2 psi of boost, would act like a big
block 470 engine at atmospheric. Kind of like dynamite, a big bang in a small package. Project:Flat-head
is going to be a Twin Turbo-Charged engine, so we need to calculate a few more items. It a huge misconception
to think Twin turbo-chargers are inherently more powerful then a single turbo set-up, as too many other factors are involved.
On in-line 4-6 and 8 cylinder engines a single turbo may in-fact be the best way to go. Usually over 350cid, and on
any "V" type engine design, the dual turbo set-up is necessary. The particular arrangement of the V-8 0r V-6
engine makes twin-Turbo's more of an attractive lay-out in terms of not only aesthetics but also thermal efficiency.
A lot of energy (heat) is lost trying to tie the two exhaust manifolds together for a single turbo lay-out. Space and
Plumbing need also be considered.
Turbos produce Huge amounts of Torque - and Torque is FUN!!
On Project:Flat-Head we are using Twin T3/T4 T04E Turbo-Chargers. These HYBRID turbochargers consisting of a T3 turbine section, (standard, Stage
II or Stage III trim) and a T4 compressor section (T04B trim or T04E trim). The T3/T4 HYBRID’s offers the low inertia
and fast boost response of the light weight T3 turbine wheel and the high airflow characteristics of the T4 compressor family,
making the T3/T4 HYBRID the turbo of choice for high performance applications. Thats all great, but what is LOW INERTIA
and FAST BOOST RESPONSE ?
Inertia
- The tendency of a body to resist acceleration; the tendency of a body at rest to remain at rest or of a body in straight
line motion to stay in motion in a straight line unless acted on by an outside force. Resistance or disinclination to
motion, action, or change.
On a turbo engine we have to consider the time it takes for the compressor to get going fast enough to make boost. This
small delay between the throttle opening and the engine making boost is know as Lag, and inertia has everything to do with
it. As the definition describes inertia, it's the resistance to change. And when you open the throttle, you
want change, and quickly! Lets look at a few different scenarios. Moment of inertia is the resistance of a rotating body to a change in speed, represented by the letter
I. I = K2M
where K is the radius of the gyration and M is the mass of the
body. Radius
of gyration is the distance from the rotating axis to the point where all the mass of the body could be located to have the
same I as the body itself.
In other words, a 12-inch diameter turbine wheel might be represented by a ring with a diameter of 7 inches. In this
case, K = 3.5 inches. For good rotor acceleration it is important to have the smallest moment of inertia possible.
Most turbine wheels are designed with minimal material near the outside diameter to reduce K. The moment is proportional
to the square of K, so reducing K by 1/2 will reduce 1 to 1/4 of the previous value. Because of this, it is often to your advantage to use two (2) smaller turbos rather then
one (1) larger turbo. Example:
On Project:Flat-Head
we are using two (2) turbos and the major diameter of one of the turbine wheels is 2.319" with an assumed weight of .89
lb's. the computation works out as follows. I = K2M I
= K2wg 1.15952 x .89lb
386 I = 0.003099 in-lb-sec2
If
we were to use a larger single turbo set-up the out come would look more like this, a single T-72 with a 4.030" turbine
wheel and a weight of 1.65lb. I
= K2M I = K2wg
2.0152 x 1.65lb
386 I = 0.017355 in-lb-sec2
An increase in time of over 5.6 times !!
Why do Turbo-Chargers
make so much Power??.. And Why so much Torque??..
Engines operate because of cylinder pressure, the amount of energy given off by the explosion of the fuel/air mixture in the
combustion chamber. For example: a cylinder with a bore area on 10 square inches (3.569 inch bore) with 800 psi
of pressure would be subject to a compressive power load of 8000 pound. This means with that 800 psi of pressure,
there would be 8000 lb of force pushing down on the piston, and it's connecting rod. That's a lot of force.
With a Turbo-Charged engine it is very easy to surpass this 800 psi threshold. Turbo-Charged engines can make up to
1600 psi of cylinder pressure, which is double the stock pressure. Even at 1200 psi, you can see that the same engine
with the same bore area, would now have a compressive load of 12,000 lbs. Thats a huge amount of force pushing down
on the piston. This is why Turbos make so much torque, the extra cylinder pressure directly equates to more compressive
power and that to more torque. While turbos are famous for extra Horse-Power, It's the Torque that really makes
them fun. Understanding
an A/R Ratio - basically the A/R is nothing more then a comparison of exhaust flow,intake volume verses discharge
area. Our A/R ratio is .63
This is
a Compressor Map of our Turbo-Charger, you can plot the map by simply plugging in our figures. As you will see, this
Turbo will work very well for our application. To make any sence out of this chart, we must first
convert or CFM figures to LB/MIN. To do this we multily the CFM by 0.069. or LB/MIN = CFM x 0.069 Engine (a) LB/MIN = 341.38 x 0.069 = 23.55 23.55 / 2 = 11.77 lb/min P/R = 1.49
Engine (b) LB/MIN = 487.04 x 0.069 = 33.60 33.60 / 2 = 16.80lb/min P/R = 1.994
Because we are useing two (2) Turbo-Chargers, we will have to split the CFM rating or you can just split the LB-MIN rating.
Too plot the Compressor map simply find the right P/R on the left side of the map and the appropiate LB/MIN figure on the
bottom. Extend the two lines and where the contact each other, is the spot at which you'll find their capacity and
the opperating RPM at which they will be. It doesen't take an expert to see that the top map (which is of the compressor
we have) is not exactly ideal for our engine. By contrast, the compressor map of the much smaller T3 compressor is much
closer to a match for our purposes. To correct this, we will change out the compressor housing with a smaller T04E "40".
This will put us back into the area we need to be. This concluded our calculations for Project:Flat-Head, we now have everything needed to install the correct Turbo-Charger and make any necessary
adjustments so the system works at it's best. The following Definitions, Tables, formulas and Information is provided
for your use and or entertainment. Hopefully this will answer the many questions one might have. The following
provided by Mega-Squirt, is from there website and included because they make a wonderful product that allows many people
to convert from a carbureted engine to EFI at a reasonable cost, with all the advantages and adjustability of the more higher
priced systems. Don't follow the crowd and think just because a system is less expensive, that is is in some way
lacking sophistication. Mega squirt, offers everything needed to run, adjust and tune a EFI engine, turbo-charged or
not, and has been proven on road-race circuits, drag strips and city streets all across the USA. FORMULAS, DEFINITIONS and TABLES
Additional information about rigid media:
Virtually all formulas and tables presented here have to do with how the
media performs. It's cooling efficiency, static pressure drop across the media relative to the face velocity and
cubic feet per minute of air flow is the measuring rod to which we apply all other calculations and determinations. In
simpler terms, the rigid media is the heart and soul of evaporative cooling. Without an understanding of it's operation,
it is difficult to design a cooling system or size cooling equipment for a building. The part about applications and design are covered in the section "Applications and Design"
which can be reached from the Technical Data section which is available from our home page. To keep a surprisingly complex
subject simple, only the formulas and tables that relate to this media are covered in this section. Abbreviations
and Definitions: Let's start
with some abbreviations we use in our formulas: AC = Air Changes (
Usually expressed in changes per hour or per minute. Air change is the number of times the air within a structure is
exhausted and replaced during a specified period such as hour or minute). Absolute Pressure
- This term refers to th pressure measured on the scale that
has it's zero point at approximately 14.7 psi (at sea level) below atmospheric pressure. it is a true measurement
of all the pressure, rather than just the pressure above atmospheric. Absolute Temperature -
Similar to absolute pressure, absolute temperature has its zero point where no heat exists. This is approximately 460°f
below 0°f. An absolute degree is the same size as a Fahrenheit degree. The freezing point of water (32°f)
is about 492°f above absolute zero, or 492° absolute. Air/Fuel
Ratio (AFR) - AFR is the ratio of the weight of
air to the weight of fuel in a combustible mixture. AFR is critical in the proper functioning of an engine.
Ambient -
Ambient refers to the surrounding atmospheric pressure and temperature. Atmospheric - This word has recently taken
on the connotation of an engine operating without any form of super-charger. My lawn mower has an atmospheric engine.
Boost - Boost
is the pressure above atmospheric, measured in the intake manifold. Boost Threshold - Same as Boost Point. This is
the lowest engine RPM at which the turbo-charger will increase power over the engines atmospheric equivalent. More simply
put, the lowest RPM at which noticeable boost can be achieved. Bypass Valve - The bypass valve permits a bleed of flow
around the turbo-charger when the engine is under boost. BTUH = British
Thermal Units per Hour. A measure of heat or the absence of heat ("cold" can be defined as the absence
of heat) in a volume of air or space. BTUH is not commonly used in evaporative cooling terminology but necessary to calculate
heating and mechanical refrigeration. (It is most often used as "heat of vaporization = 1043 BTU/lb in the formula
for calculating evaporation rate and standard CFM). Clearance Volume - Combustion chamber volume above the piston at top dead center is called clearance
volume. (S)CFM = (Standard) Cubic Feet per Minute. Usually referred to as simply CFM. This is a
necessary ingredient in any formula involving evaporative cooling. It is a measure of air volume movement in one minute.
Compression
Ratio - This is the displacement volume plus clearance volume divided by the clearance volume.
Compressor
- For this writing, the compressor is the air pump itself. The front half of the turbo-charger, through which
the intake air passes. it is also frequently refereed to as the " Cold side" of the turbo-charger.
Compressor Efficiency (Ec)
- Efficiency is the ratio of what really happens
to what should happen. In the case of the compressor, measurement of the temperature gain caused by compressing the
air exceeds what thermodynamic says it should be. Compressor efficiency converts calculated temperature gains to real
temperature gains. Compressor Surge - Compressor surge occurs when the throttle is slammed shut and air is caught
between a pumping turbo and the throttle plate. This air blasts its way backward out the front of the turbo-charger.
When this happens, there is a suddenly room for more air in the manifold, and air is pumped back in my a still pumping turbo-charger.
The throttle is still closed, so the air again blast back out through the front of the turbo. This continues until the
turbo losses enough speed for leak back around the compressor to dampen the air oscillations. Compressor surge can als
occur under boost, if too much boost pressure is present with low airflow through the system. The chirping sound heard
from the turbo when lifting off the throttle while operating under boost results from the oscillating air volume. This
noise is suppressed by the bypass valve. Crossover point - This is the point at which manifold
boost pressure equals turbine inlet pressure. Detonation - Detonation is spontaneous combustion of the air/fuel mixture ahead of the flame
front. When pressure and temperature exceeds that required for controlled combustion, the mixture auto-ignites.
The metallic pinging sound is the resulting explosion's shock wave colliding with the cylinder walls.
Design - This term
is used in many ways to define the parameters of an application or specifications. Some common uses are as follows:
IDb = Indoor Dry Bulb. ODb = Outdoor Dry Bulb. IWb = Indoor Wet Bulb. OWb = Outdoor Wet
Bulb. EDb = Entering Dry Bulb. LDb = Leaving Dry Bulb. EWb = Entering Wet Bulb. LWb = Leaving Wet Bulb.
This term is often used in conjunction with "conditions" such as "Climate Design Conditions". In
evaporative cooling, climate data is considered to be Dry Bulb and Wet Bulb levels. It would require a "Psychometric
Chart" to locate the juncture of the Dry Bulb and Wet Bulb lines to find the grains or pounds of moisture per pound of
dry air or relative humidity (RH). Refer to Table 1 for a psychometric chart digitalized for easy reading of relational
elements of Db, Wb and RH. Displacement Volume - is defined in several ways: 1.
The swept volume of the cylinder; 2. The area of the bore times the length of the stroke; 3. Total engine displacement divided
by the number of cylinders. Draw-Through - This indicates that the throttle is on the inlet side of the turbo compressor.
Dry Bulb temperature (Db or DB)
- Measurement (usually in Fahrenheit) of temperature taken by a standard thermometer or similar thermal
indicator. End
Gas - The end gas is the last part of the air/fuel mixture to burn. It's importance to a turbo-charged
engine is paramount, because it is this end gas in which detonation usually occurs. External Static Pressure - Expressed in inches,
water column. The pressure against which the air flow must move. The pressure external to the cooling unit opposing
air flow (i.e. restrictive ductwork, etc.)
Fahrenheit (f or F) - Temperature conforming to a thermometric scale
on which water boils at 212 degrees and freezes at 32 degrees. Named after Gabriel D. Fahrenheit, 1736. Fv (or) FV = Face Velocity - Face velocity or "air
velocity" is the measure expressed in feet per minute (FPM) the air is moving at the entry side (face) of the cooling
media. This is another necessary ingredient in any formula in evaporative cooling to determine efficiency. FPM = Feet Per Minute -
The measure of speed (velocity) of the air . Gallons per Hour (GPH) - A measure of liquid (usually water) moving
during one hour.
Gallons per Minute (GPM) - A measure of liquid (usually water) moving in one minute. IN. HG - This phrase reads
" Inches of mercury" and is the measure of pressure on yet a different scale. In this project, in-Hg
will reefer to vacuum in the intake manifold, and the scale works downward toward atmospheric pressure. For example,
idle speed vacuum is usually about 18in.Hg, and as throttle is applied, the vacuum goes toward 0 gauge, which is atmospheric
pressure.
Inertia
- The tendency of a body to resist acceleration; the tendency of a body at rest
to remain at rest or of a body in straight line motion to stay in motion in a straight line unless acted on by an outside
force. Resistance or disinclination to motion, action, or change. Inter-cooler -
An inter-cooler is a heat exchanger placed between the turbo and the engine to remove heat from the air exiting the turbo-charger
when operating under boost. Inter-cooler are also called charge air coolers. Inter-cooler Efficiency (EI)
- An Inter-cooler's efficiency is measured by how much heat it removes relative to the heat added
by the compressor. Inertial Load - Internal loads are those created by weight and acceleration. A heavier
piston creates a greater inertial load. likewise, an increase in RPM means greater acceleration and, thus a greater
inertial load. Lag
- Lag is the delay between a change in throttle and the production of noticeable boost when engine RPM
is in a range in which boost can be achieved. Lean - lean means not enough fuel to achieve the correct
air/flue ratio for the existing conditions. Non-sequential
Fuel Injection - EFI that pulses independently of valve position is non sequential. OEM - Original Equipment
manufacturer; the company the built it in the first place. Power
- Strictly speaking, power is the result of how fast a certain amount of work is done. In automotive context,
power is the product of torque at any specific RPM times that RPM. Power Load
- This is the load induced into all engine components by pressure created by the burning gases.
Pre-Detonation - This is a meaningless phrase and should
not be included here or anywhere else. Pre-Ignition
- Pre-ignition refers to spontaneous combustion of the air/fuel mixture prior to the spark.
Pressure ratio - The ratio of absolute boost
pressure to atmospheric pressure. Pulse Duration -
The amount of time, measured in thousandths of a second (msec), that an electronic fuel injector is held open on any single
pulse. Pulse duration is a relative measurement of the amount of fuel delivered to one cylinder per combustion cycle.
Reversion - Reversion occurs when some of the burned
exhaust gases are pushed back into the combustion chamber and intake system during valve overlap. This is caused
by exhaust manifold pressure exceeding intake pressure or by shock waves in the exhaust ports and manifold.
Relative Humidity (RH) - Expressed in percent.
The percent of water vapor in the air compared to the amount of water vapor the same air could contain. (i.e.
15% RH indicates the air is 15% saturated with water vapor) Rich
- A condition that exist when too much fuel is present to achieve a maximum -power air/fuel ratio. Saturation Efficiency (SE) - This is the
percent of the Wbd (Wet Bulb Depression) achieved by the cooling process. I.E. At 100 degrees (f) Dry Bulb and 70 degrees
(f) Wet Bulb, the Wbd would be 30 degrees (f). If the actual temperature drop measured at the discharge side of the
media was 73 degrees (f), the percent of saturation efficiency would be 90%. This means that the air passing through
the media has been saturated with water vapor (moisture) to 90% of its maximum. "Cooling Efficiency" is the
same as Saturation Efficiency and is most often used to define the performance level of the media. Also called just
"efficiency". Sequential Fuel Injection -
A fuel injection pulse timed to discharge fuel when the intake valve is in the most advantageous position is called sequenced.
It pulses the injectors in the same sequence as the firing order. Static Pressure Drop - Expressed
in inches, water column. The amount of pressure required to push the air through the media as measured with a magnehelic
gage. The difference between the pressure of the air flow at the intake of the media and the discharge side of
the media. The measure of pressure for any component through which air flow is measured at the intake and discharge. This
is an important consideration in some evaporative cooling applications. Supercharge -
To force more into an engine than the engine can breathe by itself is to supercharged it. A supercharger is a device
that does this, it may be driven by belts, gears or a turbine. When driven by a turbine, it's called turbocharging.
Thermal Load - On this
site, we will take the rather narrow definition of heat added to the system by the turbo-charger. This comes from heat
produced in the air that is compressed by the turbo and the mixture heat increase due to reversion. Throttle Response - A change in the speed and torque
of an engine brought about by change in the throttle position is called throttle response. Torque - The amount of twisting force provided by a turning shaft is called torque. It is
measured in foot-pounds, inch-pounds and even Newton-meters. Turbine
- The turbine is a fan driven by the engine's exhaust gases. it is often called the "hot" side of
the turbo-charger. Turbo-Charger -
A turbo-charger is a super charger driven by a turbine. Under Boost
- When a system has greater than atmospheric pressure in the intake manifold, it is operating under boost.
Volumetric
Efficiency (ev) - This is the ratio of the number of molecules of air that actually get into
a combustion chamber to the number of molecules in an equal volume at atmospheric pressure. Waste-gate - The waste-gate
is a boost-pressure -activated valve that allows only enough exhaust gas into the turbine to achieve desired boost.
The waste-gate routes the remainder of the exhaust gas around the turbine and out the tailpipe. Water gauge or Water Column in Inches ( WG or w.g. or WC or w.c.) This
is a measure of static pressure. A Pilot Tube is used to take this measurement. The Pitot Tube is a curved (U-shaped)
glass tube with a prescribed amount of water and a scale. The tube is hollow. When air is blown into one end the water
column will be forced up the other side to some level. The level to which the column of water rises is a measure, in
inches, of the pressure of the force required. Wet Bulb Temperature
(wb or WB) - The lowest temperature that can be reached by evaporatively cooling the air. This
measurement is usually taken with a "sling psychrometer". This device is a standard thermometer with a "wet
sock" over the sensor bulb. The psychrometer is slung in a circular motion rapidly enough to cause evaporation
to occur around the sensor bulb to drop the temperature to it's lowest point possible with the evaporation process. Wet Bulb Depression (wbd or WBD) - The difference between the Dry Bulb and the Wet Bulb
temperatures. This temperature is the total amount of cooling available through the evaporative cooling process. At
100% cooling efficiency, the temperature drop would be equal to the Wet Bulb Depression. Also known as Wet Bulb Differential.
|
 |
Leaving Dry Bulb = [ODb - (SE
x (Odb-OWb)] Leaving Wet Bulb = Normally considered same as entering Wb. Wet
Bulb Depression = ODb - OWb Evaporation Rate = [CFM x WBd x (SE / 8700)] ( this
is simple method) Bleed - Off Rate = Evaporation Rate x .20 (prox) (Recirculation) Water
flow Rate = 3 times the evaporation rate (prox) Standard CFM = Sensible BTU/hr
/ (1.08 x (IDb - Db) x Density Ratio Where
IDb = Indoor Design Dry Bulb (f) CFM = Standard CFM / Density Ratio BTU = CFM
X Delta T x 1.08 Density Ratio = 1.325 x Barometric Pressure / (Db(f)
Water weight (US gallon) = 8.33 pounds per gallon (based on distilled water) Water
volume (US gallon) = 7.481 gallons per cubic foot Water weight (US gallon cubic foot) =
7.481 x 8.33 = weight of cubic foot of water (62.288#) Face Area = Width x Height
of open face area through which air will flow (expressed in square feet.) Face
Velocity = CFM / Face Area (Sq Ft) (expressed in Feet per minute (FPM).
Table 1: Psychrometric Chart
#H20
per #Dry Air | Temperature (Dry Bulb degrees f) |
|---|
40 | 50 | 60
| 70 | 80 | 90 | 100 | 110 | 120 |
|---|
| Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% | Wb | RH% |
|---|
.001 | 27
| 20 | 34 | 12 | 41 | 10
| 46 | 8 | 51 | 5 | 54
| 3 | 57 | 2 | 62 | 2
| 65 | 1 | .002
| 32 | 40 | 36 | 28 | 43
| 19 | 47 | 12 | 53 | 10
| 57 | 7 | 60 | 5 | 63
| 4 | 66 | 2 | .003 | 35
| 58 | 41 | 40 | 45 | 28
| 50 | 19 | 54 | 15 | 58
| 10 | 62 | 7 | 65 | 6
| 67 | 3 | .004
| 36 | 75 | 43 | 51 | 47
| 38 | 52 | 26 | 56 | 19
| 59 | 13 | 63 | 10 | 66
| 8 | 69 | 5 | .005 | 39
| 95 | 45 | 65 | 50 | 47
| 54 | 32 | 57 | 23 | 61
| 17 | 64 | 12 | 67 | 9
| 71 | 7 | .006
| x | x | 46 | 78 | 51
| 55 | 55 | 39 | 59 | 27
| 63 | 20 | 66 | 15 | 69
| 10 | 72 | 9 | .007 | x
| x | 49 | 91 | 53 | 64
| 57 | 45 | 61 | 31 | 65
| 24 | 67 | 18 | 70 | 12
| 73 | 10 | .008
| x | x | x | x | 55
| 73 | 59 | 51 | 63 | 36
| 66 | 28 | 68 | 20 | 71
| 14 | 74 | 11 | .009 | x
| x | x | x | 56 | 82
| 60 | 57 | 64 | 41 | 67
| 30 | 70 | 22 | 72 | 16
| 75 | 13 | .010
| x | x | x | x | 57
| 90 | 62 | 63 | 65 | 46
| 68 | 33 | 72 | 25 | 74
| 18 | 76 | 14 | .011 | x
| x | x | x | 60 | 99
| 64 | 70 | 66 | 50 | 70
| 36 | 73 | 27 | 76 | 20
| 77 | 15 | .012
| x | x | x | x | x
| x | 65 | 76 | 67 | 55
| 71 | 40 | 74 | 29 | 77
| 22 | 78 | 17 | .013 | x
| x | x | x | x | x
| 66 | 83 | 69 | 59 | 72
| 44 | 75 | 31 | 78 | 24
| 80 | 19 | .014
| x | x | x | x | x
| x | 67 | 90 | 70 | 63
| 74 | 47 | 76 | 33 | 78
| 26 | 81 | 20 | .015 | x
| x | x | x | x | x
| 69 | 95 | 72 | 68 | 75
| 50 | 77 | 36 | 79 | 27
| 82 | 21 | .016
| x | x | x | x | x
| x | 70 | 99 | 73 | 72
| 76 | 53 | 78 | 39 | 81
| 29 | 83 | 22 | .017 | x
| x | x | x | x | x
| x | x | 74 | 76 | 77
| 57 | 79 | 42 | 82 | 31
| 83 | 23 | .018
| x | x | x | x | x
| x | x | x | 75 | 80
| 77 | 59 | 80 | 45 | 82
| 33 | 84 | 24 | .019 | x
| x | x | x | x | x
| x | x | 76 | 85 | 78
| 62 | 81 | 47 | 83 | 35
| 85 | 25 | .020
| x | x | x | x | x
| x | x | x | 77 | 90
| 80 | 65 | 82 | 49 | 84
| 37 | 86 | 27 | .021 | x
| x | x | x | x | x
| x | x | 78 | 95 | 81
| 69 | 83 | 51 | 85 | 39
| 87 | 28 | .022
| x | x | x | x | x
| x | x | x | 79 | 99
| 82 | 72 | 84 | 53 | 86
| 40 | 87 | 29 | .023 | x
| x | x | x | x | x
| x | x | x | x | 83
| 75 | 85 | 55 | 87 | 41
| 88 | 31 | .024
| x | x | x | x | x
| x | x | x | x | x
| 84 | 78 | 86 | 58 | 88
| 42 | 90 | 33 | .025 | x
| x | x | x | x | x
| x | x | x | x | 85
| 81 | 87 | 60 | 89 | 43
| 91 | 34 | .026
| x | x | x | x | x
| x | x | x | x | x
| 86 | 85 | 88 | 62 | 90
| 44 | 92 | 35 | .027 | x
| x | x | x | x | x
| x | x | x | x | 87
| 88 | 89 | 65 | 91 | 46
| 93 | 36 | .028
| x | x | x | x | x
| x | x | x | x | x
| 88 | 91 | 90 | 67 | 92
| 47 | 94 | 37 | .029 | x
| x | x | x | x | x
| x | x | x | x | 89
| 95 | 91 | 69 | 93 | 49
| 95 | 39 | .030
| x | x | x | x | x
| x | x | x | x | x
| 90 | 99 | 92 | 71 | 94
| 51 | 95 | 40 |
Notes: Db is Dry Bulb temperature, Wb is Wet Bulb temperature,
#H2o is Pounds of moisture per pound of dry air which is a measure of absolute humidity. RH is Relative Humidity.
Read the chart by finding the known elements, such
as Dry Bulb and Relative Humidity and move horizontal to find the Wet Bulb and pounds of moisture per pound of dry air. I.E.
The weather forecast is for 100 degrees at 15% Relative Humidity. You will find that the Web Bulb is 66 degrees and
the pounds of moisture is .006 per pound of dry air. Knowing the Wet Bulb will allow you to determine the Wet Bulb depression.
The Psychometric chart will provide you
the necessary information to design systems, predict outcomes and many other useful applications of the information! This
chart is digitalized to make it simpler to use. It
is necessary to interpolate and extrapolate accordingly for those in-between conditions not directly covered in the above
chart. I.E. if 105 degrees was the temperature to use, then it would be necessary to interpolate the available data
to reach the right conclusion. In this instance, the Wet Bulb would be 67.5 degrees. This chart is intended to
be reasonably accurate at sea level and should be within p/m 5%. If greater accuracy is required, it is recommended
that you use the proper Psychometric chart for the elevation desired or make proper adjustments for elevation (barometric
pressure). Table 2: Evaporation Rate
Wbd(f)
| Gallons
Per Hour evaporated per 1000 CFM with a Saturation Efficiency of: |
|---|
| 0.80
| 0.82 | 0.84 | 0.86 | 0.88 | 0.90 | .092 | 0.94 | 0.96 | 0.98
|
|---|
| 5 | 0.50 | 0.51 | 0.52 | 0.53
| 0.55 | 0.56 | 0.57 | 0.58 | 0.60 | 0.61 | | 10 | 0.99 | 1.02 | 1.04 | 1.07 | 1.09
| 1.12 | 1.14 | 1.17 | 1.19 | 1.22 | | 15 | 1.49
| 1.53 | 1.56 | 1.60 | 1.64 | 1.68 | 1.71 | 1.75
| 1.79 | 1.83 | | 20 | 1.99 | 2.04
| 2.09 | 2.14 | 2.19 | 2.23 | 2.28 | 2.33 | 2.38
| 2.43 | | 25 | 2.48 | 2.55 | 2.61
| 2.67 | 2.73 | 2.79 | 2.86 | 2.92 | 2.98 | 3.04
| | 30 | 2.98 | 3.05
| 3.13 | 3.20 | 3.28 | 3.35 | 3.43 | 3.50 | 3.58
| 3.65 | | 35 | 3.48 | 3.56 | 3.65
| 3.74 | 3.82 | 3.91 | 4.00 | 4.08 | 4.17 | 4.26
| | 40 | 3.97 | 4.07
| 4.17 | 4.27 | 4.37 | 4.47 | 4.57 | 4.67 | 4.77
| 4.87 | | 45 | 4.47 | 4.58 | 4.69
| 4.80 | 4.92 | 5.03 | 5.14 | 5.25 | 5.36 | 5.48
|
To determine Gallons per
Minute divide by 60. Formula to determine evaporation rate is shown in Formulas section. Table 3: Temperature drop across media (@ 500 FPM face velocity)
| Wbd (f) | Temperature drop (Dry Bulb) for Media Thickness of: |
|---|
| 4" | 6" | 8" | 12"
| 18" | 24" |
|---|
| 10.0 | 5.3
| 6.8 | 7.9 | 8.9 | 9.8
| 9.9 | | 12.5 | 6.6
| 8.5 | 9.8 | 11.1
| 12.2 | 12.3 | | 15.0 | 7.9 | 10.2 | 11.8 | 13.3 | 14.6
| 14.8 | | 17.5 | 9.2 | 11.9 | 13.8
| 15.6 | 17.1 | 17.3 | | 20.0 | 10.5 | 13.6 | 15.8
| 17.8 | 19.5 | 19.7 | | 22.5 | 11.8 | 15.3 | 17.7
| 20.0 | 21.9 | 22.2 | | 25.0 | 13.2 | 17.0 | 19.7
| 22.2 | 24.4 | 24.7 | | 27.5 | 14.5 | 18.7 | 21.7
| 24.4 | 26.8 | 27.2 | | 30.0 | 15.8 | 20.4 | 23.6
| 26.7 | 29.3 | 29.6 | | 32.5 | 17.1 | 22.1 | 25.6
| 28.9 | 31.7 | 32.1 | | 35.0 | 18.4 | 23.8 | 27.6
| 31.1 | 34.1 | 34.6 | | 37.5 | 19.7 | 25.5 | 29.5
| 33.3 | 36.6 | 37.0 | | 40.0 | 21.1 | 27.2 | 31.5
| 35.6 | 39.0 | 39.5 |
Note: 12" thick media @ 500 FPM face velocity is the
preferred design . This is the best trade-off between performance and cost. Table 3: Air Density Ratio:
Density Ratio for Various Elevations and Temperatures.
| Temp. | Elevation/Inches Hg |
|---|
| (f) | 0/ 29.92 | 1000/ 28.86 | 2000/ 27.82 | 3000/ 26.82 | 4000/ 25.84 | 5000/ 24.90 | 6000/ 23.98 | 7000/ 23.09 | 8000/ 22.22 | 9000/ 21.39 | 10000/ 20.58 |
|---|
| 68
| 1.00 | 0.97
| 0.93 | 0.90
| 0.87 | 0.84
| 0.80 | 0.77
| 0.75 | 0.72
| 0.69 | | 70
| 1.00 | 0.96
| 0.93 | 0.90
| 0.86 | 0.83
| 0.80 | 0.77
| 0.74 | 0.71
| 0.69 | | 72
| 1.00 | 0.96
| 0.93 | 0.89
| 0.86 | 0.83
| 0.80 | 0.77
| 0.74 | 0.71
| 0.69 | | 74
| 0.99 | 0.96
| 0.92 | 0.89
| 0.86 | 0.83
| 0.80 | 0.77
| 0.74 | 0.71
| 0.68 | | 76
| 0.99 | 0.95
| 0.92 | 0.89
| 0.85 | 0.82
| 0.79 | 0.76
| 0.73 | 0.71
| 0.68 | | 78
| 0.99 | 0.95
| 0.92 | 0.88
| 0.85 | 0.82
| 0.79 | 0.76
| 0.73 | 0.70
| 0.68 | | 80
| 0.98 | 0.95
| 0.91 | 0.88
| 0.85 | 0.82
| 0.79 | 0.76
| 0.73 | 0.70
| 0.68 |
Table
4: Air Changes suggested per hour.
| Leaving Air Temp (LDb) |
| Temperature
over outside ambient |
| Air
Changes Per Hour |
|---|
| | | | Over 78 (f) | | 20+ | | 30-60
| | 76f to 78f | | 15 to 20 | | 20 to 40 | | 74f
to 76f | | 10
to 15 | | 15
to 30 | | 72f to 74f | | 5 to 15 | | 12 to 20 | | Less than 72f
| | Less than 10
| | 10 to 15
|
Notes: The "Air
Change" method is a practical approach to assist in the determination of the size and efficiency of evaporative
cooling equipment required for the structure. The principle behind this method is to determine the difference between
the inside temperature of the structure, without using evaporative cooling and the outside ambient temperature during its
highest condition. While this method is ideal for existing structures, new structures not yet built can be estimated
on the same scale. Leaving Air Temperature reflects
the output of the evaporative coolers whether existing or planned. The air change column indicates a range of frequency
and is used in determining air volume requirements. Other criteria are needed to complete the sizing of equipment. Refer
to the section on "Applications and Design" for more specific information on equipment sizing. Acronyms / Terminology A/R
A/R
describes a geometric characteristic of all compressor and turbine housings. It is defined as the inlet cross-sectional area
divided by the radius from the turbo centerline to the centroid of that area. Compressor A/R - Compressor performance is largely insensitive
to changes in A/R, but generally larger A/R housings are used to optimize the performance for low boost applications, and
smaller housings are used for high boost applications. Usually there are not A/R options available for compressor housings.
Turbine
A/R - Turbine performance is greatly affected by changing the A/R of the housing. Turbine A/R is used to adjust the flow capacity
of the turbine. Using a smaller A/R will increase the exhaust gas velocity into the turbine wheel, causing the wheel to spin
faster at lower engine RPMs giving a quicker boost rise. This will also tend to increase exhaust back pressure and reduce
the max power at high RPM. Conversely, using a larger A/R will lower exhaust gas velocity, and delay boost rise, but the lower
back pressure will give better high RPM power. When deciding between A/R options, be realistic with the intended vehicle use
and use the A/R to bias the performance toward the desired power-band.
Choke Line The choke line is on the right hand side of a compressor
map and represents the flow limit. Properly sizing a turbo is important to prevent the compressor from operating past the
choke line. When a turbocharger is run deep into choke, turbo speeds increase dramatically while compressor efficiency plunges
(very high compressor outlet temps). Additionally, the turbo's durability is compromised by the resulting high thrust
loads.
CHRA (Center Housing &
Rotating Assembly) The CHRA is essentially a turbocharger minus the compressor and turbine housings
Clipped Turbine Wheel When an angle is machined on the turbine
wheel exducer (outlet side), the wheel is said to be "clipped". Clipping causes a minor increase in the wheel's
flow capability; however, it dramatically lowers the turbo efficiency. This reduction in efficiency causes the turbo to come
up on boost at a later engine speed (ex. increased turbo lag). High performance applications should never use a clipped turbine
wheel. All Garrett GT turbos use modern unclipped turbine wheels.
Corrected Air Flow
When plotting actual airflow data on a compressor map, the flow must be corrected to account for
different atmospheric conditions that affect air density.
Example: Air Temperature (Air Temp)
- 60°F Barometric Pressure (Baro) - 14.7 psi Engine air consumption (Actual Flow) = 50 lb/min Corrected
Flow= Actual Flow SQR([Air Temp+460]/545)/ Baro/13.95 Corrected Flow= 50*SQR([60+460]/545)/ 14.7/13.95 = 46.3 lb/min
Efficiency Contours
The
efficiency contours depict the regional efficiency of the compressor stage. When sizing a turbo, it is important to maintain
the proposed lug-line with a high efficiency range on the map. Free-Float
A free-floating turbocharger has no Waste-gates device. This turbocharger can't control its own boost
levels. For performance applications, the user normally must install an external Waste-gates.
GT
The GT designation
refers to Garrett's state-of-the-art turbocharger line. GT-series turbos use redesigned bearing systems and modern compressor/turbine
aerodynamics. These new compressor and turbine wheels represent huge efficiency improvements over the old T2, T3, T3/T4, T04
products. The net result is increased durability, higher boost, and more engine power over the older T-series product line.
On-Center
Turbine Housings On-center turbine
housings refer to an outdated style of turbine housing with a centered turbine inlet pad. The inlet pad is centered on the
turbo's axis of rotation instead of being tangentially located. Using an on-center housing will significantly lower the
turbine's efficiency. This results in increased turbo lag, more back-pressure, lower engine volumetric efficiency, and
less overall engine power. No Garrett OEM's use on-center housings.
Pressure Ratio Ratio of absolute outlet pressure divided by absolute inlet
pressure Example: Intake manifold pressure (Boost) = 12 psi Pressure drop, inter-cooler (DPIntercooler)
= 2 psi Pressure drop, air filter (DPAir Filter) = 0.5 psi Atmosphere (Atmos) = 14.7 psi at sea level PR = (Boost + DPIntercooler+ Atmos) / (Atmos-DPAir Filter) PR = (12 + 2 + 14.7) / (14.7 -.5)
= 2.02
Surge Line
The
surge region, located on the left-hand side of the compressor map, is an area of flow instability typically caused by compressor
inducer stall. The turbo should be sized so that the engine does not operate in the surge range. When turbochargers operate
in surge for long periods of time, bearing failures may occur.
Trim
Trim is an area ratio used to describe both turbine and compressor wheels. Trim is calculated
using the inducer and exducer diameters. Example: Inducer diameter = 88mm Exducer diameter = 117.5mm Trim = Inducer2/Exducer2 Trim = 882/117.52 = 56 Trim As trim is increased, the wheel can support more air/gas flow.
Waste-gates A Waste-gated turbocharger includes an integral
device to limit turbo boost. This consists of a pneumatic actuator connected to a valve assembly mounted inside the turbine
housing. By connecting the pneumatic actuator to boost pressure, the turbo is able to limit its maximum boost output. The
net result is increased durability, quicker time to boost, and adjustability of boost.
PW = REQ_FUEL * VE * MAP * E + accel + Injector_open_time
So, find the REQ_FUEL that corresponds to your
injector's flow rate and engine size. There is a REQ_FUEL calculator in Mega Tune, and also here. If you have the engine running , you can check the MAP at
idle (or you can guess - pick about ~25 kPa for a stock cam, ~35 kPa for a performance cam, ~45 kPa for a race cam). Then
you only need the idle VE (and injector open time) to predict the idle pulse width, since this is minimum when there are no
enrichments (E=0, accel=0). Note that you need to use the 'downloaded' REQ_FUEL, which is adjusted for the number
of injectors and their staging. A
good "rule of thumb" for idle VE is 30%. You may actually be 20% or 40% depending on things like compression, overlap,
ignition timing, etc., but 30% will be close enough to give you a good idea about idle pulse width. And use 1.0 msec for the
injector So, find the REQ_FUEL that corresponds to your injector's flow rate and engine size. There is a REQ_FUEL
calculator in Mega Tune, and also here. If you have the engine running , you can check the MAP at
idle (or you can guess - pick about ~25 kPa for a stock cam, ~35 kPa for a performance cam, ~45 kPa for a race cam). Then
you only need the idle VE (and injector open time) to predict the idle pulse width, since this is minimum when there are no
enrichments (E=0, accel=0). Note that you need to use the 'downloaded' REQ_FUEL, which is adjusted for the number
of injectors and their staging. A
good "rule of thumb" for idle VE is 30%. You may actually be 20% or 40% depending on things like compression, overlap,
ignition timing, etc., but 30% will be close enough to give you a good idea about idle pulse width. And use 1.0 msec for the
injector
PW = REQ_FUEL * VE * MAP * E + accel + Injector_open_time So, find the REQ_FUEL that corresponds to your injector's flow rate and engine size. There is a REQ_FUEL
calculator in Mega Tune, and also here. If you have the engine running , you can check the MAP at
idle (or you can guess - pick about ~25 kPa for a stock cam, ~35 kPa for a performance cam, ~45 kPa for a race cam). Then
you only need the idle VE (and injector open time) to predict the idle pulse width, since this is minimum when there are no
enrichments (E=0, accel=0). Note that you need to use the 'downloaded' REQ_FUEL, which is adjusted for the number
of injectors and their staging. A
good "rule of thumb" for idle VE is 30%. You may actually be 20% or 40% depending on things like compression, overlap,
ignition timing, etc., but 30% will be close enough to give you a good idea about idle pulse width. And use 1.0 msec for the
injector So, find the REQ_FUEL that corresponds to your injector's flow rate and engine size. There is a REQ_FUEL
calculator in Mega Tune, and also here. If you have the engine running , you can check the MAP at
idle (or you can guess - pick about ~25 kPa for a stock cam, ~35 kPa for a performance cam, ~45 kPa for a race cam). Then
you only need the idle VE (and injector open time) to predict the idle pulse width, since this is minimum when there are no
enrichments (E=0, accel=0). Note that you need to use the 'downloaded' REQ_FUEL, which is adjusted for the number
of injectors and their staging. A
good "rule of thumb" for idle VE is 30%. You may actually be 20% or 40% depending on things like compression, overlap,
ignition timing, etc., but 30% will be close enough to give you a good idea about idle pulse width. And use 1.0 msec for the
injector
identify your injectors by looking on: http://www.geocities.com/MotorCity/Pit/9975/dataBySubject/Injectors.html or http://www.telusplanet.net/%7Echichm/tech/injectors.pdf Injectors should not be used at more than
80-85% duty cycle. However, injector rates are always specified at 100% duty cycle and some nominal pressure (usually 43.5
psi = 3 atmospheres). The manufacturer leaves it up to you to determine a system pressure and maximum duty cycle in order
to compute the resulting flow. Injectors
are driven by an electrical signal from Mega Squirt that grounds the +12 volt supply through the injectors to open them. Once
they are open, they flow at a constant rate until closing. The amount of time required to open and close the injectors is
specified in Mega Squirt as the 'Injector Opening Time' (usually about 1.0 msec). Here is an example of a low impedance
injector's pulse voltage, current, and fuel flow:
Injectors
should not be used at more than 80-85% duty cycle. However, injector rates are always specified at 100% duty cycle and some
nominal pressure (usually 43.5 psi = 3 atmospheres). The manufacturer leaves it up to you to determine a system pressure and
maximum duty cycle in order to compute the resulting flow. Injectors are driven by an electrical signal from Mega Squirt that grounds the +12 volt
supply through the injectors to open them. Once they are open, they flow at a constant rate until closing. The amount of time
required to open and close the injectors is specified in Mega Squirt as the 'Injector Opening Time' (usually about
1.0 msec). Here is an example of a low impedance injector's pulse voltage, current, and fuel flow:
Pulse Width Modulation Injectors
are either high impedance or low impedance. High impedance injectors (usually about 12-16 ohms) can take a 12 supply directly,
without a form of current control. Low impedance injectors (generally below 3 ohms) require some form of current limiting.
With Mega Squirt, you can use resistors to limit current, or you can use Pulse Width Modulation (PWM), which is a software
solution built in to Mega Squirt.
PWM works by switching the 12 volt ground
to the injector on and off very rapidly (in about 0.000059 seconds!). The ratio of the "on" time to the "off"
time determines the current through the injectors. However, the easiest way to think of the PWM% is as a percentage of the
supply voltage, so 50% PWM on a 14 volt supply becomes effectively 7 volts on average, 28% would be 4 volts, etc. Remember that pulse width and PWM% are two
different things. Pulse width is the total duration of the signal whereas PWM% is the ratio of 'on-time' to 'off-time'
within the pulse. So in the above illustration, the pulse width for both is the same, but the PWM% for the first is 50%, while
for the second it is 25%. The
PWM% you will be able to use depends on the fly back circuit you have. Version 2.2 hardware generally requires about 55% to
75% PWM. Often the engine will run with lower values, but will not have enough voltage to re-start. Note that using embedded
code version 2.986 or higher will disable PWM during cranking, allowing somewhat lower PWM% values. The Fly Back Board allows you to lower the PWM% dramatically, generally to 30%
or less. It also helps close the injectors faster. With better fly back control, you can reduce injector opening times (recall that the injector
opening time is really the sum of the opening and closing times), and increase the duration of the 'controllable'
part of the pulse width (i.e. after the opening time), The important thing about the injector open time is that it sets a lower bound for the pulse
width (regardless of whether PWM is on, etc.). so if you have injector opening at 1.7ms, you cannot set it to 1.6 or anything
lower, even with VE=0. Mega Squirt assumes no fuel is injected during this time, but some is, though it is hard to calculate
how much. The longer it takes to open, the more fuel is likely injected during opening. With lower opening times (by allowing
full voltage (i.e. no PWM), you can get the injectors open quicker. Your engine will need a certain amount of fuel to run correctly at idle when fully warmed
up. If this amount is below that injected during the injector opening time, you will always be rich and have no way to lean
it out, short of reducing the fuel pressure. Note
that PWM is disabled (in v2.986 code) during cranking so the injectors get full battery voltage. This makes 'severe'
starting conditions (lower cranking voltages, etc.) less likely to result in the injectors not opening. This is not possible
with resistors, unless you devise a way to bypass them during starting (like the older cars did for the ignition coil).
When using low-impedance injectors, which are also called peak and hold injectors (P&H), you wire them in parallel. The
wiring is the same for P&H or saturated [high-impedance]. To exceed the recommended number of injectors (see below) either requires resistors in series with
each injector or a modified fly back setup. The following is a guide as to whether you need to use resistors or the fly back board: | Injector DC Resistance | Number of Injectors (total) | Mega
Squirt Hardware | PWM
Mode | High (12 -
16 ohm) | up to 12 | V2.2
| no PWM current limit | Low (> 2.4 ohm) | up to 4 | V2.2 | use PWM current limit | Low (> 2.4 ohm) | more
than 4 | V2.2 | Use injector resistors or fly back board | Low (< 2.4 and > 1.2 ohm)
| more than 3 | V2.2
| Use injector resistors or fly back board | Low (< 1.2 ohm)
| up to 2 | V2.2
| use PWM current limit | Low (< 1.2 ohm) | more than 2 | V2.2 | Use injector resistors or fly back board | One sure way to know if you can't use the standard V2.2
fly back circuit is to have a fly back failure. The circuit will most often fail after some time spend at high speeds and
loads, rather than immediately when you start the engine for the first time. Generally, when the fly back circuit fails, the
Mega Squirt works okay on the stim, but not on the car. Signs of an impending fly back failure are:
- Mega Squirt will often require higher PWM%
over time,
- The engine may
start running erratically, especially at higher speeds and loads,
- the injectors may 'stick' open and flood the engine.
When the fly back fails, sometimes Q1 (the
TIP32 on the bottom of the PCB) looks pretty rough, all burnt, etc. However sometimes it looks fine. If Q1 (on the bottom of the board) does look burnt however, this
is a sure sign of a fly back failure. To
repair after a fly back board, you need to adopt the fly back board, or use injector resistors. fly back board, or use injector resistors. To use
the fly back board, you will discard many of the original V2.2 fly back components,
so don't replace anything until you install the fly back board. However, if you are going to repair the V2.2 fly back circuit and use injector resistors, you need to replace a number of components: - Q1 - 497-2629-5-ND, ~98¢,
- U7, the 34151 FET driver IC - IXDI404PI-ND, ~$4.12,
- Q2 and Q7, the FETs - IRFIZ34G-ND × 2 for ~$1.43
each.
If you are doing repairs, you
might also get a socket for the FET driver AE7208-ND (~35¢), it ensures the FET driver sees no heat during assembly,
and makes it easier to replace in the future. The
resistors and diodes of the V2.2 fly back circuit seem to survive the fly back failure generally, though you could order and
replace them to be sure (they are reasonably cheap). They
are: - R12 and R17
- 22QBK-ND, ~28¢ for 5,
- R32
- 270H-ND, ~27¢ for 5,
- D20,
D22, and D23 - 1N4001DICT-ND ~26¢ each,
- D21
- 1N4753ADICT-ND, ~36¢ each.
In
order to prevent future flyback failures, you can adapt either the flyback board or injector resistors. The flyback board: allows the injectors to open somewhat faster than resistors
will, improve the dynamic range of the injectors (resistors added about 1.0 millisecond to the injector opening time), the flyback board gives the injectors
'full power' while cranking, potentially making for better starting when it is very cold or when your battery is marginal,
the
flyback board potentially allows you to minimize the current through the injectors by tuning, theoretically helping them to
last longer due to lowered heating of the injector coils, the flyback board and components are cheaper in some cases than resistors,
if bought new, depending on how many you have to use.
However, resistors are: - simpler,
- have
no active components to fail,
- require
little additional wiring, and
- have
been proven in millions of mid-eighties OEM applications.
For example, the injector resistors
825F7R5-ND are $4.66 each. The flyback board ($12) and components ($6.86) total $18.86, so the 'cross-over' point
is 4 injectors, using new components (depending on shipping, etc.). Of course, if you source your resistor pack from a scrap
yard, or if your vehicle already has them, this is cheaper! The Fly back Board People running a number of very low impedance
injectors have reported problems with the flyback circuit failing. Typically, this will happen with 4 or more low-impedance
injectors, such as the Holley 85 lb/hr TBI injectors. This can be avoided by using resistors in series with the injectors,
and disabling the pulse width modulation (PWM). However, a more elegant solution that continues to use PWM is the Fly back
Board. The Fly back board is
an additional 'daughter card' for Mega Squirt that does a number of things: - It provides each injector bank with a separate flyback
circuit,
- It uses 'heavy-duty'
components capable of handling higher currents and transients,
- It has a very substantial aluminum heat-sink,
- It invokes the flyback circuits only after the PWM has ended, eliminating the load on the
flyback components during PWM.
The
Fly back Board installs in the up half of the Mega Squirt case. It slides into the lowest slot, and is attached to a substantial
heat sink (that you make yourself from ½"x¾" aluminum angle). Six 20 to 22 gauge wires (two injector
banks, two CPU [X0, X1], +12 volts, and ground) connect the Flyback Board to Mega Squirt. The Flyback board must be used in conjunction with embedded code version 2.986 or higher. This code has the proper switching code to turn
the Flyback circuits on after PWM ends. This
is the schematic for the Fly Back board:
Like all other Mega Squirt kits, you order the PCB at: http://www.bgsoflex.com/mspo1.html then place an order with Digi-Key through the BOM at: http://www.megamanual.com/fbbom.htm for most of the remaining parts. To assemble the flyback board, follow these instructions: 1) Disable the existing flyback circuit. You
can do this by cutting the leads to D22 and D23. You can remove the remaining flyback components if you wish. They are: R32
(270 ohms, ½ watt resistor), Q1 (TIP42 transistor), and D21 (36 volt Zener diode). Removing components is easiest if
you cut the leads, then remove each lead separately. This puts less heat into the board and other components. 2) If you are upgrading your flyback components
because of a flyback failure, replace the 34151 FET driver IC, and the two FETs (IFRIZ34) as well. 3) Install and solder R101, R102, R103, R105, R106, and R107. All
of these are 270 ohm, ½ watt resistors {270H-ND}. 4) Install and solder R104 and R108 {1.0 Kohm, ¼ watt}. 5) Install and solder D100 and D103 {fast recovery diodes, FR302DICT-ND}.
Be sure to orient them with the banded end as shown on the silk screen. 6) Install and solder Q103 and Q106 {transistors, PN2222AD26ZCT-ND}.
Note that the flat side faces to the left when the silk screen printing is oriented so that you can read it. You have to bend
the middle leg slightly towards the flat side to fit it in the holes. 7) Install and solder D102 and D104 {36 volt Zener diodes, 1N4753ADICT-ND}.
Be sure to orient them with the banded end as shown on the silk screen. 8) Before installing the four T0-220 transistors, you need to fabricate
the heat-sink. You need two 3½" (89mm) long pieces of aluminum angle that are ½" by ¾"
(13mm x 19mm), about .040" to .080" thick (1.0mm to 2.0mm). Drill (1/8" - 3mm) these as indicated below:
Make sure your heat
sink is no longer than 3½" (89mm), so that it can sit flat against the case. The edge of the heat sink is flush
with the end of the case. Drill corresponding holes in the case. Be sure to drill the correct end of the case (the DB9/LED
end). Verify that the heat sink will sit flat when bolted to the case. The heat sink is design to attach to the FlyBack board by the four
transistor mounting holes. The heat sink should just be tall enough to allow the FlyBack board to slide underneath it when
it is installed in the lowest slot of the upper case. Make sure to get the heat sink dimensions correct - otherwise you could
stress the FlyBack board and/or impair the heat conduction abilities of the FlyBack board. Either could lead to failure.
9) Assemble the heat sink (but do not
fasten it to the case) as shown below using ½" (13mm) #4-40 machine screws and nuts: 10) Bends the leads of
the TIP125 Darlington transistors Q102 and Q105 so that the mounting holes and leads line up with both the PCB and heat-sink.
Make sure the leads of the transistor will not touch the heat sink! The heat sink is sandwiched between the transistor body
and the PCB. Apply
heat sink compound between the two angles, and also between the transistors, mica, and heat sink. Bolt the transistors in
place using #4-40 machine screws and nuts using a mica insulator kit between each transistor and heat sink. Be sure to place
the bolts for the transistors/heat sink through the bottom, and the nuts on the top, as clearance is limited. You might have to trim the mica with a sharp
pair of scissors to make it fit properly. Solder the transistor leads in place. Use a multi-meter on its highest resistance setting to check that
you have "infinite" resistance between the metal mounting tab of the transistor body and the heat sink. If this
is not the case, your insulator is not insulating. Find out why. You may have to de-burr the transistor mounting holes in
the heat sink (you can counter sink them with a quick touch of a ¼" drill). You can also sand the surface of the
heat sink lightly where the transistors bolt on. Be sure to thoroughly clean the heat sink afterwards. Do not proceed until you have electrically
isolated the TIP125 transistor mounting tab from the heat sink. 11) Bends the leads of the TIP32C {TIP32CFS-ND} transistors Q101 and Q104 so that the mounting
holes and leads line up with both the PCB and heat-sink. Make sure the leads of the transistor will not touch the heat sink!
Apply heat sink compound
between the two angles, and also between the transistors and heat sink. Bolt the transistors in place using #4-40 machine
screws and nuts. These transistors do not need a mica insulator. Be sure to place the bolts for the transistors/heat sink
through the bottom, and the nuts on the top, as clearance is limited. Solder the leads in place. 12) Run a 20 to 22 gauge jumper wire from X0 on the Mega Squirt PCB
(near the CPU) to X0 on the Flyback PCB. 13) Run a 20 to 22 gauge jumper
wire from X1 on the Mega Squirt PCB (near the CPU) to X1 on the Flyback PCB. 14) Run a 20 to 22 gauge jumper 12 volt power wire from the unmarked
through hole just to the right of X13 (and slightly below) on the Mega Squirt PCB to the hole marked 12V
on the right side of the FlyBack PCB. 15) Run a 20 to 22 gauge jumper ground wire from the unmarked through any of the holes for the 'non-banded'
end of the unused diodes (at D1, D2, D3, or D4) on the Mega Squirt PCB to the hole marked GND on the right side of the FlyBack
PCB. For example, if you use D4, install the ground wire from the end of D4 closest the CPU to the hole marked GND on the
FlyBack PCB. 16 a.)
Connect a 20 to 22 gauge wire from the hole at the non-banded end of D22 (the one you removed) on the Mega Squirt PCB to the
hole on the Flyback PCB marked INJ1. 16
b.) Connect a 20 to 22 gauge wire from the hole at the non-banded end of D23 (the one you removed) on the Mega Squirt PCB
to the hole on the Flyback PCB marked INJ2. 17) Install the heat sink and FlyBack board into the case. The board
slides in the first slot in the case. Apply heat sink compound between the case and heat sink. Use #4-40 screws to fasten
the heat sink. You may need to bend any of C12, C15, C17, C18, C19, C22, C23, and/or C24 over a bit to get enough clearance,
depending on how much lead length you left when they were originally soldered in. 18) Make sure to load version 2.98 embedded code or higher into your Mega Squirt. 19) Reset your PWM parameters. Try 30% and 1.0ms to start, then "tune"
them as described in the manual. 20) Reassemble your case, and you are ready to go! Be careful not to 'pinch' any
of the connecting wires between the two halves of the case when you reassemble. Note, if you assemble your flyback board, but find that it won't
allow your engine to run with less than ~75% PWM, the flyback board is NOT working. You need to find out why. You can:
- Go over the manual again, and verify
the each component and it's orientation, if applicable,
- Check all the soldered joints and connections,
- Verify that the board is getting a good ground,
- Verify that the board has 12 volts,
- Verify
the signals at the X0, X1, INJ1, and INJ2 connections (with an LED tester and the Mega Squirt on a stim),
- Verify that there is 'infinite' resistance between the TIP125s
and the heat sink,
- Verify that the
connections are to the correct place on the boards (both flyback and Mega Squirt),
- Verify that you have V2.98+ embedded code (reload if necessary).
If it passes all those tests, you have to start looking at individual
components. Often, the flyback board is installed because of a failure, in which case the FETs and FET driver should probably
be replaced as well.
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Injector Resistors However, instead of
the flyback board, you may choose to use resistors in series with your injectors. Several people reported that resistors do NOT result in significantly
longer opening times, or any other troublesome effects, so this is a good solution for many installs. To eliminate PWM altogether,
use a 5 to 8 ohm resistor (with a 20 to 25 watt rating) in series with each injector. If you want to avoid using PWM with your low-impedance injectors,
you can use ballast resistors in series with the injectors. You should use one resistor (20-25 Watts) in series with each
injector, otherwise the injectors may not all draw the same current, and the failure modes become complicated and difficult
to diagnose. As well, you would need a very large resistor to handle more injectors. For example, if you allowed 2 Amps through
four 1.2 Ohm injectors wired in parallel (0.3 Ohms total) to one 7 Ohm resistor, the power dissipated would be: P = V * I = 12.5 Volts * 2 amps
x 4 injectors = 100 Watts! If
you use resistors that limit injector current to less than 2 amps, you can disable the PWM mode (by setting PWM% to 100%,
and time threshold to 25.4msec) and treavolts Requiredt the system as high-impedance. To limit the current to under 2 amps,
you need: resistor ohms
= (alternator voltage / 2.0 amps) - injector resistance For
example: resistor ohms
= (14.0 volts / 2.0 amps) - 1.2 ohms =>
resistor ohms = 7.0 - 1.2 = 5.8 ohms You
can also use the calculator below. Enter your injector resistance in ohms, your hold current in amps, as well
as your injector impedance in ohms, in the form below and press the "Compute resistor" button. Injector
resistance (ohms) | Hold current (amps) usually
~1 or 2 amps | Supply voltage (volts) usually
~14 volts | Required Resistors (ohms)
| | | | |
The 25-watt resistors aluminum case Ohmite resistors (with 1% tolerance) from www.digi-key work well. Below is a picture of a 7.5 ohm resistor, Digi-Key
part number 825F7R5-ND. Ohmite has several suitable resistors, with part numbers that start 825F (25 Watt, aluminum case
with mounting ears) and end in XRY, where X and Y indicate X.Y ohms. Depending on injector, pick 2-8 ohms or so. You may be able to use less resistance to protect
the flyback components - just a few ohms combined with PWM may do the trick. Be sure to use one resistor in series with each
injector, and then you can parallel these into the two banks. Do not share two or more injectors per resistor, use a resistor
per injector. There a lower bound to the pulse width, below which a low impedance injector cannot be expected to reliably function. There are
two problems with running the very lower pulse widths that result from large injectors. There is a limit on the physical ability
of the injector to opening and close as quickly as possible, and there is also a limit to the ability of the Mega Squirt controller
to adjust the pulse width to an optimum value at very low pulse widths. The absolute physical limit depends on your particular injectors
and the hardware that controls them. Some are able to go as low as 1.1 to 1.5 milliseconds [ms]. Note that there are three
components to the injection duration - the opening time, the commanded pulse, and the closing time. Ideally you would want
the opening and closing times to be a short as possible to have the controller determining as much of the amount of the time
injected as possible. The opening time is difficult to adjust given a certain operating voltage. The closing time, however
is controlled to a degree by the flyback circuit in the Mega Squirt. With very large injectors [for a given application], the idle pulse widths may be around
1.0 millisecond. This is a problem because in the standard code for Mega Squirt, the resolution of the steps is 0.1 ms. So
a 1.1 millisecond “squirt” will only be able to be adjusted in ~9% increments (i.e. 1.0, 1.1, 1.2 etc.), which
may be too coarse to get a good idle. The high-resolution Mega Squirt code can help in this situation, but you lose the PWM
current limiting mode so you have to run resistor packs with peak and hold low-impedance injectors. An ideal idle duration is around 2.3 ms, and
this is approximately where properly sized injectors should operate. This gives good resolution [~4%], and you should be able
to get a real good idle. You
will need to acquire connectors for wiring the Mega Squirt to your injectors, etc. Niehoff has individual injector connectors
under part number 28419 (connector) and 28418 (sealing boot). On the web, Waytek has lots of different connectors that you
can use in building your Mega Squirt. Their prices are about as cheap as you can find. The injector connectors are AMP part
number 827551-3, but sometimes you have to buy a large quantity. Also try DelCity. They are not quite as cheap, but they may
have stuff you cannot get from Waytek. Injector Bungs You can
get information on injector bungs for port injectors by checking out www.sdsefi.com for injector/manifold installation information, along with
lots of other great information. The bungs are 0.530"-0.535" inside diameter [about 17/32" or 13.5 mm]. The
fuel supply lines for the top of the injectors are the same size. VERY IMPORTANT! If you do not own at least two fire extinguishers, go buy some right now!
Experimentation with EFI can be very dangerous because you are playing with high pressure gasoline. Install at least one fire
extinguisher in your work area (away from where the fire is mostly likely to occur) and carry another one in your car. Do
not ignore this advice. We do not want to be visiting you in the hospital or worse! MSD and others have an “Epoxy-In Pocket” fuel injector
bung as PN 2120 (set of 8). Holley also offers them as PN 534-83 for a four pack (~$50), 534-84 for a pack of six (~$72),
or 534-85 for a pack of eight (~$94). These bungs can be held in place with epoxy or welded and is used for fixed fuel rail systems only. These
bungs are CNC-machined from aluminum for precise dimensions and have a ¾” OD. Internally, the pockets are contoured
to accept the bottom sealing O-ring of a standard injector. MSD also has “Thread-In Pockets”. The aluminum pockets
will screw into a ¾”–16 hole and are supplied with a #8 O-ring to seal the pocket to the manifold. PN 2125
gets a set of 8. Fuel Rails Most
injector systems will use one or more fuel rails. These serve two functions: they supply fuel to a multiple number of injectors
(4 on a 4 cylinder, for example), and they physically locate the tops of the injectors. Most OEM rails can be made to work
with standard engine configurations, but if you are doing a custom conversion you may have to fabricate fuel rails. Many place
supply blank aluminum fuel rail extrusions in whatever length you need. One example is Ross Machine. They have two styles of fuel rail extrusion. They can also
create custom fuel rails for you, with the injector holes placed to suit you. The aluminum extrusion comes in two sizes: - Dash 10 (.800" Bore) - $10/foot, and
- Dash 6 (.500" Bore) - $12/foot.
For fabricating fuel rails,
MSD has “Fuel Delivery Top Mounts”, PN 2115, set of 8. These fuel delivery mounts are CNC machined from #304 stainless
steel for great durability and precise dimensions. They slide over ½” steel tubing (MSD PN 2205) then are brazed
or TIG welded in place to form a fuel rail. Fuel is routed through a 5/16” hole aligned to the mount and the injector.
The PN 2105 Fuel Rail Clip is required for assembly. Their “Stainless Steel Fuel Tubing”, PN 2205, comes in 2
four feet lengths of 304 stainless steel tubing, and is perfect for making custom fixed rails. The seamless tubing has a ½”
OD and .035” wall. Throttle Bodies Your throttle
body choice depends on whether you are going to use throttle body injection or port injection. Your throttle body needs to do 2 things: - control the amount of air going into the engine, and
- report the throttle position to Mega Squirt via a
TPS.
For
port injection, you can convert an existing carb, to do both jobs - the carb already controls the air flow, you have to adapt
a TPS sensor to it. You may choose to machine out the venturis, remove the float bowls and fuel circuits if you wish, but
that isn't necessary (but may be desirable for a number of reasons, including increased power!). Some people use the complete individual runner (IR)
throttle body and injector set-ups off late model motorcycles - they often have enough flow for automotive engines, and are
frequently available cheaply on eBay. However, if you are planning on a throttle body injection set-up, you need a dedicated TBI unit (in order
to supply the fuel to the injectors, etc.), which can be hard to find for larger engines - Holley has made a 4bbl TBI for
years (in 650, 700 and 900 cfm sizes), and as the computer fails regularly on these, they are sometimes available separately
on eBay. TBIs have the advantage of having the fuel pressure regulator
built in, of course. Note
that for either port or throttle body injection you can use multiple throttle bodies to support your power levels, if your
manifold configuration can be adapted for them. However, if you are uncertain of your throttle body's application, you can measure the
throttle bore size. However, you can't really compare the throttle of an EFI throttle body to the throttles of a carb.
This is because the throttle(s) of a EFI TB is the main restriction, but on a carb, it is the venturis that are the main restriction.
So you really have to compare the EFI throttle size to the carb's venturi size. However there are also a number of other
considerations, such as that you can go larger with a EFI TB than a carb without suffering so many adverse effects because
a vacuum signal isn't needed for the EFI to operate.Fuel delivery is always good with EFI (well, mostly). When selecting
a throttle body, there are a number of considerations. You need it to flow enough to support your engine's horsepower
(or more correctly, to not restrict your engines power). Generally, you want to take the throttle body from an engine that
made similar horsepower to your engine. However,
there are some drawbacks to a too large throttle body: - At low rpm, you go from low kPa to 100kPa with very little throttle movement, making driveability
'worse'. For example, with a very large throttle body you may get 100 kPa at 20% throttle at 2000 rpm. This means
if you want to hold it at 40 kPa for cruise, I have to be very steady on the throttle, as small movements may produce large
changes in engine output (so it's harder to be smooth), and
- A small throttle movement (and a small V/sec TPS signal change) can result in a very large
change in MAP (as mentioned above) at low rpms. The result is little (or no) accel enrich when the engine needs it most. However,
you can usually tune around circumstances like this by richening the VE table at low rpms and higher kPa (say < 2500 rpm
and> 70 kPa) by about 5-7%. This has a negligible affect on fuel economy, since you likely never see 70 kPa while cruising.
For reference, the GM tuned Port Injection
engines used throttle bodies with two 48mm throttles. These support about 230 horsepower, however these throttles were not
the limiting factor in the power produced by these engines. To
calculate how much horsepower you can make from a given throttle body size, you can use the estimator below: Note that the above is for naturally aspirated
engines having a common plenum - individual runner manifolds will need larger throttle bodies, turbocharged 'blow-through'
engines can get by with somewhat smaller throttle bodies Fuel Supply System In
order to use Mega Squirt, you will have to implement a high-pressure fuel supply system. You MUST understand how to do this
properly, and this manual DOES NOT include everything you need to know. If you are unsure about your installation, have a
qualified mechanic look it over before attempting to start your vehicle. Fuel Pumps You will
need a high pressure pump with enough volume at your operating pressure to feed you engine under maximum load. Typical pressures
needed in the neighborhood of ~45 psi for port fuel injection, ~10-20 psi for TBI injection. A port injection pump will work
with TBI, but not vice-versa. OEMs usually place pump inside the fuel tank.
In an EFI retrofit it is generally easier to use an external fuel pump. Ford used external fuel pumps on 1989 era 150 trucks
which may be a candidate for use. These are high pressure [port EFI] pumps that will work in most applications. Econoline
vans have these as well. The external pumps used in Ford F150 fuel injected
trucks from the 89-93 model years are Delco EP286. At 12 volts, the operating pressure is 70-95 PSI with 36-40 gals per hour.
The biggest Delco pump is the EP424, which is 75-90 PSI at 40 gals per hour. EP 268 is a GM# 25117086, EP 424 is a GM# 25176156."
Here is a picture of the Econoline pump:
The Carter pump #P70199 (the outlet is 7/16 standard
pipe thread and the inlet is 15/32 clamped hose type fitting or 3/4 standard thread. The specs are 95-PSI max, 68-93 G/Hr
wide open). This is the highest flowing Carter external fuel pump in the book. It will produce up to 95 psi, and crosses over
to EP7107 at Kragen for about $80 (unfortunately one end does not come off like the Carter). You might want the Ford style
pump EP7109($80). You will need this if you want to be able to modify ends to be 3/8". Others
have had luck using the external pump from various fuel injected VolksWagen models (87 VW Fox, for example). Part number is:
Bosch 0 580 254 957 reportedly rated at 90 GPH@ 70PSI, you might find them for about $130 new from www.germanautoparts.com. This pump consists of a fuel pump, filter, and an "accumulator". You can leave the accumulator
in place since it does not affect the running volume or pressure, and on used pumps they are often rusted so you might not
want to mess with it. Auto Performance Engineering has many high volume Walbro pumps (and their specifications) on their site. Fuel Line Steel tubing is recommended, but you MUST have
short sections of rubber line in the feed and return lines between the engine and frame to allow for engine movement. The
return line should have minimal restriction. For reference, GM systems typically have 3/8" feed lines and 5/16"
return lines. You may be able to use your original fuel line as a return line,
plumbing a new 3/8" (10mm) line for fuel supply. You can run the return line into the tank, or reroute it to a fitting
or nipple you install in the fuel tank filler neck/tube assembly (in which case you may be able to use the original pick-up
for your supply line). If you run a new pick-up into the tank, it will need a filter. GM sells a sock-type filter that is
a good fit for 3/8" lines. It is part number 5651702 and costs about $15. You
may have to fabricate fuel lines for your system. Tubing is available in steel, stainless steel, and aluminum for this purpose.
The size is generally given as the outside diameter of the tubing. Unless you have a very unusual combination (or very high
horsepower, well over 500+), you should be able to use 3/8" tubing for both the supply and return lines. Buy a good tubing bender (there are numerous styles in various price ranges) so that you don't kink or
collapse the tubing while bending it. (You can also bend it over a V-belt pulley, in some cases.) The AN (Army-Navy) 'dash' system of hose and fitting sizing was established many years ago by the
American military as a common measurement for hoses and fittings. It designates the outside diameter of the metal tube that
is compatible with each size of fitting. The AN dash measure is the standard for performance hose applications. These dash
sizes are expressed in 16th of an inch. For example, an -06 fitting is 6/16 of an inch or
3/8", just right for our fuel lines! Most fittings
and adapters in the automotive aftermarket are based on a 37° sealing angle (SAE J514 37° - formerly known as
JIC). These are also often referred to simply as AN fittings. Male and female 37° fittings will mate together for
a leak-proof connection. | SAE J514 (37° AN) | | Dash Size | Inch Size | Nominal Thread Size | | 04 | 1/4 | 7/16-20 | | 05 | 5/16 | 1/2-20 | | 06 | 3/8 | 9/16-18 | | 08 | 1/2 | 3/4-16 | | 10 | 5/8 | 7/8-14 |
Be
aware that there are other similar fittings and adapters that use a 45° sealing surface (SAE J512), such as those commonly
available at your local hardware store for flared copper pipe. These 45° fittings and adapters can also be found in some
OEM automotive applications. However, although they may look very similar to a 37° fitting, they are not interchangeable.
In some sizes, they may thread together (-02, -03, -04, -05, -08, -10), but will not seal properly, due to the difference
in sealing surface angles. Be sure you know the sealing angle of the fittings you are connecting! | SAE J512 (45°) | | Dash Size | Inch
Size | Nominal Thread Size | | 04 | 1/4 | 7/16-20 | | 05 | 5/16 | 1/2-20 | | 06 | 3/8 | 5/8-18 | | 08 | 1/2 | 3/4-16 | | 10 | 5/8 | 7/8-14 |
Abrasion
(the rubbing of the hose against some other component) is the number one cause of hose failure. A leaking fuel hose can start
a very dangerous fire in your car, so make sure hose assemblies are routed properly to reduce the chance of any abrasion damage.
Use a support every 12 to 18 inches (30 to 45 cm) to secure the hose. For chafe protection, be sure to install a grommet at
any point a hose passes through a panel or bulkhead. Besides steel or aluminum
tubing fuel line, you can also use one of the steel or nylon braided hoses from various suppliers. Generally these use the
same AN 'dash' sizing system, and can use appropriate fittings to connect to 37° flare, NPT thread, or other systems.
Note that if you are using a factory fuel rail, you may be able to find an aftermarket
adapter to mate your OEM fuel fitting to an AN hose. For example, Accel offers TPI fuel rail fittings (pn 74730, ~$32) for
-06 hose that will fit most General Motors TPI fuel injections systems. If you
need a simple way to get to a barbed fitting to connect up rubber EFI hose to the General Motors 2 bbl TBI, your local auto
parts house probably stocks GM fuel line repair kits in the HELP section. These consist of 9" of steel fuel line in 3/8"
and 5/16" outside diameter with an O-ring and Saginaw fittings 14/16 mm, respectively, on one end and a barbed end crimped
on the other. The steel lines are about $4.00 each. These pieces thread into the steel adapters on the GM Rochester TBIs.
For a complete listing of various fittings with part numbers, etc. try: http://www.ag.auburn.edu/users/gparmer/efi/fittings.txt IMPORTANT: Keep the fuel lines out of passenger compartment and routed
safely away from moving or hot parts to avoid damage/excessive heat. For flexible rubber hose use the SAE 30R9 EFI hose which
is rated at 250 psi. EFI hose clamps are also recommended rather than gear clamps. Check with someone who knows if you are
not sure about your installation. Nobody needs a 50 psi gasoline fed fire to ruin their day! Note that if you feel your fuel supply is not smooth enough, you can add an accumulator. OEMs often have
nice small diaphragm types, or you can plumb in a vertical section of rubber hose tee'd off the supply line (and plugged
at the top end). This traps air and uses it to cushion the fuel pressure. Here
is a GM style accumulator (it is about 2" (50mm) long and uses 3/8" tubing): Or you can make your own: Fuel filter Use a fuel
injection fuel filter rated for the pressure at which your system operates. DO NOT use a universal carburetor
filter - the higher pressure of fuel injection systems may cause it to burst! Position the filter downstream of the
pump so that a clogged fuel filter will not over heat the fuel-cooled pump. Fuel
Pressure Regulator The vacuum referenced fuel pressure regulator is essential.
It provides constant pressure differential between fuel at injector nozzle and manifold air pressure [port EFI] or atmospheric
pressure [TBI]. This makes the injected fuel quantity solely a function of the injector open time. If you were to 'cap off' the manifold vacuum port on the fuel pressure regulator, you are reducing
the dynamic range of the injectors. This means you will need lower pulse widths at at (giving less control over idle mixtures)
and lower flow under boost (restricting the maximum horsepower). So, in general,
for port injectors, have the fuel pressure regulator connected to the manifold vacuum is a good thing. There is very little
reason not to do it (though some have argued against it for individual runner port EFI set-ups). If you have an adjustable fuel pressure regulator (FPR), set the pressure with the fuel pump running, but
the engine not running - that's your base fuel pressure (it is referenced to atmospheric pressure). The regulator is typically at the far end of the fuel rail (after the injectors), but performs its job anywhere,
so long as it is after the fuel pump. However, if you have the regulator before the rails, then the full volume of fuel isn't
circulating through the rails. Only the amount of fuel actually injected moves, and the fuel can get quite hot, which may
require special injectors, etc. Apparently OEM use special injectors, etc., with returnless systems, which is essentially
what one has if they put the regulator before the injectors. This can also create problems trapping air on assembly that can
cause issues at first start-up. If you are using an aftermarket fuel pressure regulator, it is a good idea to also
install a pressure gauge, since most of these are adjustable. For TBI, use a 0-30 psi gauge. For port injection use a 0-60
psi or 0-100 psi gauge. Most of these gauges will mount directly on a fuel fitting using a 1/8"
NPT thread. These are available from most aftermarket speed parts suppliers, such as Summit Racing or Jegs. Surge Tank
You only need a surge tank if you are using a low pressure pump to supply an external high-pressure
pump. Some pumps come with an accumulator after the pump, and these can be left in place. Wiring the Fuel Pump To activate the fuel pump, Mega Squirt provides a ground for the fuel pump relay circuit on pin 37. The relay
is wired for 12 volts switched from the ignition switch, and the relay is grounded through Mega Squirt [pin 37 on the DB-37
connector]. Mega Squirt will disable the fuel pump when RPM = 0 and enable while
non-zero (cranking/running), except for Version 2.00 (and up) embedded software which will perform a short priming pulse,
then shut down the pump if the engine is not running after 2 seconds. You might
want to consider a safety switch in the fuel pump circuit when installing an electric fuel pump. Holley has one (12-810, ~$20)
that will ensure the fuel pump will not run unless the engine has oil pressure. It stops the pump from running if the motor
stalls with the ignition on. Wiring the switch through the starter solenoid circuit energizes the pump on engine start-up.
Once the engine has started, the switch continues to provide power to the pump as long as there is oil pressure to keep the
switch turned on. Note: An inertial safety shut off switch should be installed
and used to kill power to the pump upon significant impact to vehicle. These
switches are available in junk yards from EFI Fords. The switch is on the drivers side in the trunk, near the trunk hinge,
mounted so that it is between the interior bracing and the rear quarter panel (protected from being knocked around if you
stuff your trunk full of stuff). It is mounted with the reset switch straight up. Note switch mounting orientation probably
matters. It is Ford Part # F2AB-9341-AA. The wire going into it is about
14 gauge, so it should be capable of handling the full current of the fuel pump. The
markings on the switch show that it has NO/NC (normally open/normally closed) positions so that it should be able to accommodate
any possible fuel pump configuration. Last Updated: 09/01/2007 12:05:18 Last Updated: 08/30/2007 13:05:27 Last Updated: 08/30/2007 10:38:48 Last Updated: 08/29/2007
20:17:01 Last Updated: 08/29/2007 15:36:55 Last Updated: 08/29/2007 14:51:16 Last Updated: 08/29/2007 12:34:16 Last Updated:
08/28/2007 23:00:44 Last Updated: 08/28/2007 17:54:26 Last Updated: 08/28/2007 17:03:54 Last Updated: 08/28/2007 16:33:05
Last Updated: 08/28/2007 09:02:18 Last Updated: 08/27/2007 22:17:10 Last Updated: 08/27/2007 21:52:09 Last Updated: 08/27/2007
21:26:56 Last Updated: 08/27/2007 21:16:20 Last Updated: 08/26/2007 22:02:28 Last Updated: 08/19/2007 18:42:30 Last Updated:
12/24/2006 20:30:05 ©2004, 2005 Bruce Bowling and Al Grippo. All rights reserved.
Project FlatHead......Part 3 Click Here
Pro Weld
5937 Ethan Drive
Burlington, KY 41005
859-586-4069
Proweld@myway.com
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